Air pump



July 17, 19281.

J, F. JAWOROWSKI AIR PUMP 5 sheets-sneer l Filed Dec. 4, 1922 ||\VENTOR JFwoHaM/sfr/ 144A/wr- July 17, 1928. Y 1,677,780

J. F. JAwoRowsKl AIR yPUMP Filed ne.4.1'9 22 s Sheets-sheet 2.

IOL-l 'Z BY ATTORNEYf July' 17, 192s. 126713730 J. F.' .mworaowls'm` AIR PUMP FiledDe'c, 4. 1922 v 5 Sheets-Sheet 3 5- NVENTOR JFJAwoRows/r/ M' mvv/Lfmm ATTORNEYS Patented duly i7, 182g..

PATENT orrics.

JOSEPH F. JWOROWSKI, 0F CLEVELAND, OHIO.

AIR PUMP.

y Application filed December 4, 1922. Serial No. $04,708.

rlhe primary object of the present invention is to provide a rotary machine adapted to compress air to a high degree and in an ecient manner. rlo achieve this object I provide a perfectly balanced smooth-rolling piston adapted to revolve at a highspeed within a circular compression chamber, and also provide an oscillatory member to co-act with said piston increating and maintaining a. high pressure. The machine is particularly designed lto operate with a minimum of friction and to facilitate lubrication of the interior operating mechanism. rlhe compressor is also `particularly con- 'i structed to eliminate air voids and pockets;

to permit accurate and convenient assembly and disassembly of the parts; to prevent leakage; to facilitate repairs and replacements; and to promote durability and along operating life without loss in efficiency.

lin the annexed drawings, Fig. 1 is a horizontal section of my improved compressor on line 1-1 of Fig. 2, and Fig. 2 is a vertical section on line 2 2 of Figs. 1 and 5.

Fig. 3 is a perspective view of the rotor pist-on, and Fig. t a perspective view of the oscillatory abutment. Fig. is a vertical section on line 5 5 o Fig. 7. Fig. 6 is a perspective view of the rear packing plate. Fig. 7 is a vertical section on line 7--7'of Fig. 5. Fig. 8 is a horizontal section on llne 8-8 of Fig. 7, showing the lubricatin device. Fig. 9 is a sectional view and e evation orn the rotor shaft and rotor assembly. Fig. is a vertical section on line 10-10 of Fig. 5. Fig. 11 is a perspective view of the packing ring used in the front cover plate. Fig. 12 is a side elevation of the complete compressor.

rlhe compressor comprises a round castinetal body 1 having a hollow rectangular base portion 2 provided with lateral supporting legs 3. rlhe exterior of .body 1 1s provided with a series of heat-radiating and strengthening ribs 4and the front side of this body is finished fiat and smooth to seat a cover and bearing plate 5 opposite ar cir` cular compression chamber 6 which extends approximately half way into the body. A circular chamber 7 is provided within the rear side of body 1 opposite the vertical division wall 8 centrally within said body. A. hub 9 extends from wall 8 into `the rear chamber 7 and a relatively large round open ing in this hub is adapted to receive a ballbearing ring 10 in clip seating position against an annular fiange 11 extending from the end face of the hub toward the axis of the opening, see Fig. 5. The front side of wall 8 is iat and smooth except where slightly dished or recessed at 12 annularly around the front projecting end of ring 10, and this shallow annular recess 12 serves as a receiving and l distributing space into which oil or grease may be introduced under pressure by way of a valved nipple 14 located in an exposed and accessible place at thecircular side of body 2. In Figs. 7 and 8, this lnipple is shown as communicating with a horizontal duct 15 in middle wall 8 having a discharge outlet 16 opening at right angles into annular recess 12.

The inner circular surface compression chamber 6 is constantly engaged by a rolling member 17 having the form of a flat ring of the same width as the depth of said chamber and the plane end fnaces 18-18 ofthis ring are adapted to rub against or travel in close proxmnty tothe flat side of wall 8 and the Hat face of cover plate 5, see Fig. 5, and which plate also provides a support for a ball-bearing ring 19 of the same diameter as ring 10. Plate 5 is provided with a flanged boss 20 to seat ring 19 in the same slip way as ring 10 is held and seated, and an annular flange 21 extends forwardly from plate 5 a substantial distance to provide a circular chamber 22 of relatively the same size and diameter as chamber 7. These end chambers are closed tightly, the front chamber 22 by a rabbeted plate or disk 23 removably secured to flange 21 by screws 24, and the rear chamber 7 by a packing plate 25 .screwed or bolted to the rear side of body 1. Packing .late 25 is so-called because it` has a screw-t ireaded extension 26 provided with a central shaft opening and packing recess 27, and a packing follower or gland 28v is seated within recess 27 and held adjustably in place therein by a screw cap 29 engaged with extension 26. The bottom of extension 26 is provided with a longitudinal channel 30 open at one end to the interior of screw cap 29, and the follower or gland 28 has an annular recess 31 inside which is also open to the interior of the cap by way of an outlet 32, see Fig. 5. In this way the oil or grease is prevented from escaping at the rear side of the screw cap where the exposed end of the rapidly revolving shaft l ing contact with 33 would scatter' it, and is instead caused to flow inte the cap and to escape through channel 3() where it can drip into a receiver it it is desirable orneeessary to collect it.

Shaft 33 has slight enlargements34-34 upon which separate ball-bearing rings 35-35 are sleeved with apress fit 20-so as to revolve with the shaft, and a series of steel balls 36 are conined between these rings and the larger rings 10 and 19 at opposite sides of the rolling member' or piston 17. A still larger ball-bearing ring 37 is slipped but not tightly into a centrally contractedv portion 38 in piston 17 directly opposite and .surrounding a second ball-bearing ring 39 tightly tted upon a flanged crank or eccentric portion 4() of shaft 33, and a series of heavy steel balls 41 is interposed between the two rings 37 and 39, respectively, to promote a noiseless and friction-reducing drive means for the rolling piston, whereby the piston will have an orbital travel within compression chamber 6 and a constant rollthe .smooth circular wall of said chamber. Tn rotating shaft 33 in a given direction the rolling piston is ot course carried with it and caused to have an orbital travel in the same direction, but because its peripheral tace is constantly in contact with the circular wall of chamber 6 the piston is also caused to rotate on its own true axis in an opposite direction to its orbital movement. The centrifugal tendency et the piston in its rapid revolution also causes it to positively engage the circular surface of the chamber and to maintain and assure a closely sealed rolling lit at all times regardless of wear at the bearings.

ln order to utilize this rolling orbital movement of the piston for compressing air to a high degree and to the best advantage I employ an oscillatory member 43 having a curved abutment extension 44 adapted to project into chamber 6 in constant bearing engagement with the peripheral face of the piston. The air is taken in and discharged on opposite sides of extension'44, and the intake passage 45 and the outlet port 46 are situated in such close proximity and definitely predetermined relations in respect to this extension and the circular rolling boundary for the piston that absolutely no air pockets or voids will be created in operations. Moreover-t0 obtain a high degree of compression T have discovered that the size ot the discharge port and its position in respect to the abutment is very important. Thus it should be noted in Figs. 1 and 2, that discharge port 46 is a round opening of relatively small diameter situated approximately midway between the front and rear sides of compression chamber 6, and that the axis of this discharge port meets the intersection of the two curved surfaces a and l) repre,-y senting the circular boundary ot compression chamber 6 and the curved pressure side ot abutment 44. As piston 17 rolls toward the curved side bof the abutment the compression space is contracted more and more until no further compression space exists on that side of the abutment. ln this movement ot the piston the abutment is pressed outward to its limit when the roller is seated directly opposite the axis of the small discharge port. Tn this position of the parts there is absolutely no void or dead space between the abutment and piston and the port, but the port is practically open to the newly developed crescent-shaped compression chamber, and the compressed air just discharged through port 46 is prevented Jfrom returning because of the spring-pressed ball valve 48 seated in the flaring outlet end 49 of this port opposite a detachable discharge nipple 50, see Fig. 1..

The piston-engaging extremity ot abutment 44 is beveled on the intake side to provide a reduced or narrow contact edge 51, and a transverse channel 52 is formed in the curved pressure side of the abutment to receive a packing strip 53 having a recessed and shouldered inner side in which a dat bow spring 54 may be confined and :function to press the packing strip against the curved abutment seat 55 which has its axis or center of generation in pivot pin 56 for oscillatory member 43. This pin extends clear through the rear wall of base portion 2 where an oil or grease cup 57 may be attached thereto in an exposed and accessible position,

and a longitudinal oiling passage 58 extends axially through-the pin and has lateral outlets 59 opening into the bore of the hub of oscillatory member 43. The forward end of this member is also provided with a semi-- spherical recess 60 in which a semi-spherical head 61 .is loosely seated but nevertheless held therein by a coiled wire spring 62 sleeved over the stem 63 of this head. The lower end of this spring is seated within a cupped set screw 64 adjustably ixed within the closed bottom 65 of base portion 2, see Fig. 2and therefore the spring may be compressed and permitted to expand rapidly and faceof cover plate 5 are provided with registering annular grooves. 66 wherein a split spring ring 67 may be seated. This ring functions as a sealing' member for the joint and also as a centering device for plate 5.

lSplit balance I'weights 68-68 are clamped to shaft 33 outside of the .ball bearing and ,rotate inchambers 7 and 22, respectively,

and these balance weights areeasily reached and adjusted by merely removing the end plates 23 and 25, respectively, without disturbing the main bearings. Cover plate 5 is also provided with an air intake opening 69 opposite the compartment in hollow base 2, and a perforated guard 70 having a wire screen 7l at its inner flanged side is removably mounted within this openingv 69, see Fig. 5. In operation shaft 33 revolves at about 1725 revolutions per minute, but the roller revolves on its own axis at a much slower speed. Two hundred and fifty pounds pressure and higher can be obtained from this rotary compressor, using a cooling jacket, but the compressor can be operated continuously Without a cooling jacket and compress air from one hundred and seventy-five to two hundred pounds pressure.

What I claim, is:

A rotary air compressor, comprising a body having a circular air-compressing chamber open at one sidethereof and provided with air intake and discharge ports, a movable cover plate enclosing the open side of said chamber, said body and cover plate having circular registering grooves in their meeting faces, a splitspring ring mounted within said grooves, a rolling air-compressing member within said chamber, and a movable abutment extending into said chamber intermediate said intake and discharge ports.

In testimony whereof I ailix my signature hereto. i

JOSEPH F. JAwoRowsKI. 

